Variable-capacity controller for compressors



May 17, 1949. w. TURNWALD VARIABLE-CAPACITY CONTROLLER FOR COMPRESSORS Filed April 20, 1945 5 Sheets-Sheet 1 Wolfgang Turnwald mfwfl Fiel May 17, 1949. w. TURNWALD 2,470,380.

VARIABLE-CAPACITY CONTROLLER FOR COMPRESSORS.

Filed April 20, 1945 5 Sheets-Sheet 2 FiG. 5

Snventor Wolfgang Turnwald.

(lttorncgs May 17, 1949. w. TURNWALD VARIABLE-CAPACITY CONTROLLER FOR COMPRESSORS 3 Sheets-Sheet 5 Filed April 20, 1945 FiG.5

Snvenfor Wolfg ang'lurnwald.

C(ttomegs Patented May 17, 1949 VARIABLE-CAPACITY CONTROLLER FOR COMPRESSORS Wolfgang Turnwald, Milwaukee, Wis., assignor to Nordberg Manufacturing Company, Milwaukee, Wis., a corporation of Wisconsin Application April 20, 1945, Serial No. 589,357

8 Claims.

This invention relates to progressive capacity control for compressors having suction operated inlet valves. It is an improvement on the controller described and claimed in the patent to Nordberg, 2,134,834, November 1, 1938.

The Nordberg patent discloses a displacing unit which delivers timed hydraulic pressure impulses to motors which suspend the action of the inlet valves. The patent proposes two alternative schemes of control of such compressor inlet valves, and the present invention is adaptable to either. It will be described as applied according to the preferred scheme of operation in which the valve controllers hold the inlet valves open during the initial portion of the discharge stroke, and for variable periods. Thus the valves are allowed to close throughout the discharge stroke at full capacity. As capacity is reduced they close at points later and later in the discharge stroke until they do not close at all, when the compressor is completely unloaded.

Since the valve controllers are actuated by unidirectional timed hydraulic impulses, they must be biased, and springs are used for this purpose. The bias could act in either direction, but the preferred arrangement, here illustrated, uses controllers which are biased so as to hold the inlet valves open, and are retracted by the hydraulic impulses. This arrangement, also shown in the Nordberg patent, has the advantage that the reaction upon the valves is limited to the stress developed by the biasing spring.

Novel features of the present device, are a simple starting unloader that operates through the capacity control, a simplified pressure responsive mechanism, a simple and precise arrangement for varying the duration of impulses, and various structural details which favor economy in manu facture and render the device applicable to a considerable range of compressors.

A controller for two valves or sets of valves timed at 180 of crank angle is illustrated in the accompanying drawings, in which:

Fig. 1 is a view partly in elevation but chiefly in vertical axial section through the impulse unit. The driving connection between the shaft of the impulse unit and the compressor crankshaft is shown.

Fig. 2 is a section on the line 2--2 of Fig. 1.

Fig. 3 is a fragmentary axial section through the head of the starting unloader motor on the line 3-3 of Fig. 2.

Fig. 4 is a fragmentary section through a typical inlet valve controlling unit.

Fig. 5 is an elevation of a 2-cy1inder, Z-stage vertical compressor, having the invention applied.

Nora-Figs. 1-3, inclusive show the parts positioned as they would be at starting with no air pressure in the receiver and no oil pressure in the shaft lubricating system. Fig. 4 shows the valve controller in the position it assumes under hydraulic pressure, i. e. retracted to permit the inlet valve to close.

Refer first to Fig. 5. The compressor has a base frame 6, first-stage cylinder 1', second-stage cylinder 8, and two-throw crankshaft 9 driven by an electric motor I l whose shaft is directly connected to the crankshaft 9. The cylinders are doubleacting, and the first-stage has pairs of inlet valves I2 for each working space. The second-stage has one inlet valve I3 for each working space. This arrangement permits the inlet valves to be identical, but does not impose this as 2. requirement. A typical inlet valve is shown in Fig. 4.

Inlet valves are of the so-called reed or feather type described in the patent to Nordberg, 1,570,392, January 19, 1926. The particular embodiment thereof illustrated in the present application is illustrated and described in detail in the Nordberg Patent 2,134,834 above mentioned.

So far as is necessary for an understanding of the present invention, the valve may be described as follows:

There is a grid-like seat member l4 and a related grid-like guard member [5. The valve proper comprises strips 16 of thin steel plate and each is seated by a related bow spring ll. The yoke indicated at [8 is a part of a hold-down mechanism to retain the seat [4 in place, and is sustained by the bonnet l9. Mounted in the bonnet is a cylinder member 2| closed at its inner end and subject at its inner end to hydraulic pressure delivered through the connection 22.

A plunger 23 is connected to a yoke 24 and this is biased inward by a coil compression spring 25. The yoke 24 is adjustably connected rigidly to the push rod 26, which is guided in a portion of the bonnet and which carries at its lower end a comb 21. This includes a series of spaced bladelike fingers 28 so arranged that when the plunger 23 is allowed to move inward under the urge of the spring 25, the fingers hold the valve strips 5 away from the seat l4, and thus maintain the inlet valve open. When, however, sufficient pressure is developed in the connection 22 to overpower the spring 25, the fingers are retracted and the valve strips are free to close against the seat member M.

The details of the construction of the valve 4 are not a feature of the present invention. They are illustrated to show onetype of valve which might be controlled according to the present invention.

In Fig. 5 a cylinder lubricator 29 is indicated. It is not a part of the present invention, but since its drive is associated with the valve controller, it is identified.v

Mounted on :the endof the base '5 is the housing 3| of the impulse device, in which device are embodied the important novel features of the present invention. The details of this mechanism are shown in Figs. 1 to 3, inclusive towhichrefercnce should now be made.

The end of the shaft 9 appears in Fig. 1v and is shown as tubular. One of the main crankshaft bearings is indicated at 32. Connected to the end of shaft 9 by threaded connectors 33 are an eccentric 34 and gear 35. The eccentric 34 isens circled by a strap 36 whose rod 3! operates the lubricator 29. The gear 35 drives the pinion 38 Wbiehis. on. the. shaft ofv the oil p mp 39. The pumniiififdelivers oil under'pressure of say fifteen or. twenty pounds per square inch to passages 4| drilledin the. crankshaft; These passages deliver oilto the main bearings, the crank bearings of the compressor; etc., according to familiar practime in thepart.

An extension of the passage '41 formed within the, eccentric 34, as shown, lubricates the eccentric strap, bearingand' also the part numbered v42" which is. the floating member of an Oldham coupling afiording a drive between the shaft 9 andLilhe actuatingshaft43 of the impulse mechanism. The shaft43 is mounted in bearings 44 which. are supported, as clearly shown in Fig. 1, by a portion of the housing 3|. The shaft 43 carries two cams 45 which are of identical contour and which are displaced-angularly 180 from each other;

The; construction of -theldham coupling is suchas to assure correct assembly. A slotted hub lfl'is'keyed on the end of-t'heshaft 43-and the slots receiverespective'lugs 4Twhich extend from the righthand face of the member 42; Projecting from the left-hand .face ofthe member 42 is a transverse rib 48 which is slida'ble in a transverse slot formed in the eccentric 34. The spring assembly show-n generally at 49 acts to hold the member 42 to the left so that it seals the end of the'iubricating portdescribed as formed in the eccentric 34. This is simply an expedient to: prevent the escape of oil. The member 42 is asymmetric to the extent that the rib 48 is not centeredon a diameter but is offset slightly so that only one assembled relation with the cocentric is possible. The purpose is to insure the intended angular relationship between cams 45 and-the shaft 9.

Thehousing '31 has abottom '1 and thus serves a areservoirwhi'ch retains a bath of oil. This oil substantially fills thehcusing, i. e. to the depth indicated by legend oil level. There is also a transverse horizontal member 52 which serves as asupport for thehydraulic cylinder uni-t hereinafterdescribed. The member 52 is not, however; a partition as free flow through it is permitted at 53'.

Whilethe impulse mechanism might include any desired number of impulse units from one a duplex unit has been chosen for description since that is the simplest embodiment which ppulcf'be illustrated and still disclose the use of a plurality of timed units.

jljiesetimedunits are essentially identical and the? description of one unit will suffice. A cylin- (her body 54 is rigidly mounted on' the member 4 52. It has two cylinder bores, one for each unit. Both cylinders are visible in Fig. 1, and one is shown in section in Fig. 2. Each cylinder is open at its lower end and is located immediately above the corresponding one of the cams 45. Through this open lower end works the large head 55 of .a difierenttial piston whose smaller or neck portion 56" works in a corresponding bushing or guide 5] fixed in the cylinder body 54. The bushings '5'! are independent and they are held in place 'by studs and nutsv50, two of which are visible in The piston made up of the parts 55-56 is axially bored to receive a timing valve 58 whose lower end controls communication between the cross ports 59 and the lower portion of the axial bore above mentioned. The lower end of the head 5.51s cross drilled at 6| to provide an escape path for oil. The lower end. of head 55 engages the corresponding cam the piston being biased into contact with the cam by a. coil compression springfii which reacts between a spring seat 63 threaded to theup-per end of neck 56 and a spring seatformed on the lower face of cover '64. The cover 64 is'remo-vaibly mounted on the top of the housing 31.

Mounted in the cylinder body 54 is a poppet type oil inlet valve 65 which coacts with a seat pressed into the body 54. The valve 65 is urged in a closing direction by a coil compression spring 66-. The spring 66 seats against a removable bushing 61' which serves as a seat for a poppet type relief valve 58-. The valve 68 is normally held: closed by a spring 59 which is housed in tubular member H and reacts at its upper end against the spring seat 12', which closes the upper end of the tubular member 11.

As explained, there are two cylinder bores and eachhas its own inlet valve 65 and relief valve 68. There aretwo tubular members 1| each with its own spring seat 12. A yoke 13 retains both these springs seats, the yoke being held by a nut '14 threaded on a stud which is shown fixed to the cylinder body 54. The working space in each cylinder is the annular space 15 above the head 5-5; It isconnected by a passage 76 with a tube H. There is a tube 1! for each impulse cylinder 15. The connection of these tubes to the inlet valve controlling motors will be described later.

To unload. the compressor at starting, recourseis had to the expedient of holding the inlet valves 65 open. .So long as these. valves remain open no impulses can be delivered through the connections 1-71, so that the springs 25 of the motors shown in Fig. 4 hold the compressor inlet valves. open continuously. To hold the inlet valves 6:5. open there is provided a shiftable spring-biased member which is allowed to force the valve open when there is no oil pressure in the passage 41 and is retracted to an inactive positionisome time after adequate oil pressure has been developed in passage 4|. This mechanism is clearly visible in Figs. 1' to 3, inclusive.

A forked member 78 is provided with fingers positioned to engage the lower ends of both valves 65. The member 18 is mounted on a stem 19 which isguided vertically in a portion of the body 54 and is biased upward by a coil compression spring 8!, which is stressed heavily enough to overpower both the springs of the two inlet valves Thus unless the stem 19 is forced downward the inlet valves are held open. The stem M will be forced downward-bye plunger 82' shortly after sufiicient lubricating pressure has been developed in the passage M. A branch of the passage 4| leads to a connection 83 at the main bearing 32. This is connected by a pipe 84 with the connection 85 which leads to the upper end of the starting unloading cylinder 8'5. A single-acting piston 81 works in the cylinder 85 and carries the plunger 82. The piston is biased upward to its inactive position by a coil compression spring 88 and the lower end of plunger 82 is spaced a considerable distance from the upper end of the stem 19, the plunger and the stem being axially aligned. Descent of piston ill full stroke will move the yoke I8 far enough to free the valves 65 and permit them to close.

It is important to delay the loading action long enough to permit the motor ii to come to speed, but it is equally important that the piston 8! return rapidly to its uppermost position when the motor is stopped, so that the compressor will be unloaded when and ii the motor is immediately restarted. The effect is secured by using an asymmetric flow connection between the pipe 84 and the working space in cylinder 86. This is arranged as follows.

A check valve 89 lightly loaded by coil compression spring 9i permits rapid back flow to the connection 85 (see Fig. 3), but a, throttling plug 92 screwed into the head of the cylinder 88 and having a restricted port 93 (see Fig. 2) greatly delays flow of oil from connection 85 to the space above the piston 81. To protect the port 93 from becoming clogged, a fine strainer M is mounted on the entrance end of the plug 92.

It follows that if the compressor is stopped the piston 81 moves up promptly upon the dissipation of oil pressure and allows the unloading yoke '18 to become effective almost immediately. When the compressor is started, however, it takes some time for the lubricating oil to move the piston 87 through its idle motion. As a result the impulse mechanism remains unloaded throughout the starting phase and for a period long enough to enable the electric motor H to come to speed. Unloading of the impulse mechanism results in concurrent unloading of the compressor.

The timing of impulses is controlled solely by the cams 45. These cams are designed to give smooth acceleration and deceleration of the plunger, and they are so designed that upward motion of the plunger 55 commences slightly in advance of the commencement of the displacement stroke of the related compressor cylinder, so that under full load conditions the fingers 28 will move clear of the inlet valve during the terminal position of the suction stroke, permitting the valve to close automatically at the very commencement of the discharge stroke. The displacing action continues for somewhat more than 180, so that the fingers 28 will be held retracted until after ensuing suction stroke has started and the valve l6 has opened. In consequence of this timing the fingers 28 at times prevent the valve from closing and then permit it to move to its seat, but they never strike it from its seat.

The duration or" such impulses is varied by varying the time at which the impulse commences. This is done by varying the position of the valve member 58. With the valve 58 in the position shown in Fig. 2, the impulse would start at the commencement of upward motion of the head 55 and would continue throughout such upward motion. If the valve 55 be lifted from the position there shown the piston 55 would have to move far enough to cause the lower margin of port 59 to overtravel the lower end of the valve 58, before the impulse would start.

The position of valve 58 (and in this connection it should be remembered that there is one such valve for each impulse cylinder) is controlled by a pressure-responsive device which will now be described. Adjustably threaded on the upper end of each valve stem 58 is a corresponding collar which is locked in position by a check nut 96. The collars 95 are engaged by a forked yoke fil' (see Fig. 2) which is vertically slidable on a guide rod 93 and which is biased in a downward direction by a coil compression spring 99. The spring 99 reacts between the yoke and the spring seat IiiI pinned to the top of the guide rod 98.

A bifurcated lever H32 straddles the yoke 91 and hinged at H83 on lugs carried by the cover The lever is loaded by a weight I06 which is clamped thereto, and may be adjusted in the direction of the length of the lever to vary its effect. Downward motion of the lever is limited by an adjustable stop screw I935. The lever carries a pair of rollers m4 which underlie the yoke 91.

Mounted between the arms of the lever I02 is a roller 531 which engages the upper end of a plunger E08. The plunger works in a cylinder I09 to the lower end of which a connection I I I leads. The connection I! I transmits to the plunger I08 the head pressure against which the compressor operates. This might be sensed at or near the discharge connection from the second-stage cylinder B, in cases where no receiver is used. Where a receiver is used, the connection would be made to such receiver.

In any event, the weight I06 determines the minimum pressure which will cause lever I02 to move upward, and the spring 99 furnishes the scale or range of graduation between full compressor capacity attained when the lever I02 is in its lowermost position and a completely unloaded state.

It will be observed that the stroke of the plunger 23 is constant but that the working stroke, i. e. the effective displacing stroke of the plunger 55, is variable being maximum when the compressor is working at full capacity. The function of the relief valve 68 is to dissipate excess oil displaced in each stroke. It follows that the strength of the spring 69 must be suffi-cient to make sure that the spring 25 (Fig. 4) is overpowered, but should not greatly exceed the necessary value. In determining the strength of the spring 69 account must be taken of friction in the flow connections.

In Fig. 5 connection 'I'I, which is the one of the two nearest the compressor, is shown connected to the branches 22 of three inlet valves. These are the two crank-end valves of the firststage and the head-end valve of the secondstage. The other impulse connection indicated in Fig. 5 as 'l'Ia controls the head-end inlet valves of the first-stage and the crank-end inlet valve of the second-stage.

Operation Assume that the compressor has been shut down and that there is no air pressure in connection II I. The parts would be in the positions shown in Figs. 1 to 3, inclusive. When the motor II starts the compressor will be completely unloaded because the yoke 18 holds both of the inlet valves 65 open. Consequently the springs 25 hold all theinlet valves 16 of the compressor continuously open.

.Assoon as the compressor has operated long enough to develop pressure in the lubrication passages 41 this pressure will be transmitted through the pipe 84 and restricted opening 93 tothe space above piston 87. The slow descent of piston 81 will ultimately force the yoke 18 downward and thus allow the inlet valves 65 to close. It has been assumed that there was no pressure in the discharge connection of the compressor. Accordmgl y, lever H12 would be in its lowermost position. The valves 58 would therefore cause their respective plungers to displace oil throughout their full strokes. Consequently the inlet valves of the compressor will be allowed to close at the beginning of the discharge stroke and remain closed throughout the discharg stroke.

If the discharge connection of the compressor should be under suflicient. pressure when the motor H starts, the lever I02 would be in some elevated positionin" which the compressor would operate at diminished capacity. Elevation of the valves 58 renders the displacing plungers .55 inefifective for the initial part of their strokes, and th extent of elevation-determines where in these strokes the plungers become efieetive.

When the motor H is-stopped, the pressure in passages 4! fades quite rapidly. The piston 87 moves up promptly because the check valve 89 permits back flow to occur without limitation by the port 93. Hence the yoke 18 becomes eifective almost immediately to open .and hold open the inlet valve 5.5 or the. impulse cylinder.

This invention provides two related but distinct functions. It provides for complete unloading during starting and a rapidresetting of this unloading mechanism if the motor be stopped even for a brief period. In addition, the invention provides an automatic variable capacity control which responds to. discharge pressure. This phase of the invention involves suspension of the operation of the inlet valves for variable periods.

While I prefer to use it as described to hold the inlet valves openduring a. variable initial portion of the discharge stroke, it can be used according to the alternate principle described in the prior Nordberg patent. The described arrangement is believed to. be preferable because the springs 25 on the inlet valves tend to establish an unloaded condition, and because the reaction on the inlet Valves is limitedto the force delivered by the springs.

Another advantage of the arrangement is that it is favorable to the incorporation of the starting unloader in that the disablement of the oil displacing mechanism assures that the compressor inlet valves; will remain in unloaded condition. The invention is applicable to more than two groups of valves simply by the duplication of the displacing units. Thus while one em- 'bodiment has been described in great detail this is intended to illustrate the principles of the invention. These principles are broader than any particular embodiment thereof, and may be incorporated in a number of mechanisms which differ in detail. The claims alone define the scope of the invention.

What is claimed is:

1. The combination of a compressor having inlet anddischargevalve's; atleast one hydraulic motor operable to control the operation of an inlet'valve; a. l rydrauli'c cylinder; a piston reeipr-ocable-in-said cylinder and defining an impulse space therein; a connection between saidimpulse space: andzsaid hydraulic motor; a valve guided in said piston, shiftable in the direction of motion of thepiston and serving by coaction with the piston to control a free vent from the impulse space, said valve being indifferent to pressure developedinthe impulse space; means responsive to pressure developed by operation of the compressor and. serving to adjust the position of said valve an inlet valve for the impulse space; a loaded relief valve for releasing excess pressure developed in the impulse space; and means for reciprocating said piston in timed relation to cycles: of the-compressor.

2. The combination of a compressor having inlet. and discharge valves; at least one hydraulic motor operable to control the, operation of an inlet valve; an open-ended shouldered cylinder; a coacting shouldered. piston exposed at both ends of said cylinder and having an axial bore communicating by lateral ports with an annular impulse chamber defined by the piston within" the cylinder; a connection between said impulse space and said hydraulic motor; a valve extending through one end of the piston, shiftable axially in said'bore with reference to the cylinder and piston and controlling said lateral ports to time venting flow from said impulse chamber; means for adjusting the position of said valve; an inlet valve for the impulse space; a loaded relief valve for relieving excessive pressure on the impulse space; and means reacting upon the other end of the piston. for reciprocating the piston in timed relation to the cycles of a compressor,

3. The combination of a compressor having inlet and discharge valves: at least one hydraulic motor operable to control the operation of an inlet valve; an open-ended shouldered cylinder; a coacting shouldered piston exposed at both ends of said cylinder and having an axial bore communicating by lateral ports with an annular impulse chamber defined by the piston within the cylinder; a connection between said impulse space and said hydraulic motor; a valve extending through one end of the piston, shiftable axially in said bore with reference to the cylinder and piston and controlling said lateral ports to time venting flow from said impulse chamber; means for adjusting thev position of said valve; an inlet valve for the impulse space; a loaded relief valve for relieving excessive pressure on the impulse space; means reacting upon the other end of the piston for reciprocating the piston in timed relation to the cycles of a compressor; a pressure motor subject to pressure developed by operation of" the compressor for operating said valve-adjusting means; and two means opposing the action of'said motor, one of which is a weight arranged to ofier' a uniform resistance to its action, and the. other of which is a spring arranged to exert a resistance which gradually increases in proportion to the adjustment effected by the motor.

4-. The combination of a compressor having inlet and discharge valves; a s'hiftable controller yieldingly biased to hold said inlet valve open; a hydraulic motor operative to shift said controller against said bias; a hydraulic cylinder; a piston reciprocable in said cylinder and defining an impulse space. therein; a connection between said space, and said motor; a valve guided in said piston, shi'ftable. in the. direction of motion of the piston. and serving by coaction with the piston to control a free vent from the impulse space; means responsive to pressure developed by operation of the compressor and serving to adjust the position of said valve; an inlet valve for said impulse space; means effective when the compressor is being started and before it attains full operative speed to hold the last-named inlet valve open; and means for reciprocating said piston in timed relation to the cycles of the compressor.

5. The combination of a compressor having inlet and discharge valves and a lubricating system which is under pressure developed when the compressor runs; a shiftable controller yieldingly biased to hold said inlet valve open; a hydraulic motor operative to shift said controller against said bias; a hydraulic cylinder; a piston reciprocable in said cylinder and defining an impulse space therein; a connection between said space and said motor; a valve guided in said piston, shiftable in the direction of motion of the piston and serving by coaction with the piston to control a free vent from the impulse space; means responsive to pressure developed by operation of the compressor and serving to adjust the position of said valve; an inlet valve for said impulse space; a loaded relief valve for releasing excess pressure developed in the impulse space; means yieldingly biased and so arranged that when free to act it serves to hold open the inlet valve for the impulse space; and a motor subject to pressure developed in the lubricating system and serving when under full lubricating pressure to overcome the bias of the last named means.

6. The combination of a compressor having :2"

inlet and discharge valves and a lubricating system which is under pressure developed when the compressor runs; a shiftable controller yieldingly biased to hold said inlet valve open; a hydraulic motor operative to shift said controller against a said bias; a hydraulic cylinder; a piston reciprocable in said cylinder and defining an impulse space therein; a connection between said space and said motor; a valve guided in said piston, shiftable in the direction of motion of the piston and serving by coaction with the piston to control a free vent from the impulse space; means responsive to pressure developed by operation of the compressor and serving to adjust the position of said valve; an inlet valve for said impulse space; a loaded relief valve for releasing excess pressure developed in the impulse space; means yieldingly biased and so arranged that when free to act it serves to hold open the inlet valve for the impulse space; a pressure motor operable to 4 shift the last named means against said yielding bias; and an asymmetric flow connection between the last-named motor and said lubricating system, arranged to permit free fiow from the motor to the system but to retard flow in the reverse direction.

7. The combination of a compressor which performs recurrent cycles; capacity controlling means cyclically adjustable to modify the volumetric efilciency of each cycle; means biasing said capacity controlling means in a compressor unloading direction; an expansible chamber motor for shifting said capacity controlling means against said bias; a cylinder; a piston reciprocable in said cylinder and defining therein an impulse space; a connection from said impulse space to said motor; a valve coacting with said piston to control a free vent from the impulse space, said valve being adjustable to vary its control point with reference to the piston stroke; means responsive to pressure developed by operation of said compressor for adjusting said valve; means for reciprocating said piston in timed relation to the cycles of the compressor; a relief valve for permitting relief of excess pressure developed in the impulse space; an inlet valve for the impulse space; and means effective under compressor-starting conditions to hold the last-named valve open.

8. The combination of a compressor which performs recurrent cycles; capacity controlling means cyclically adjustable to modify the volumetric efiiciency of each cycle; means biasing said capacity controlling means in a compressor unloading direction; an expansible chamber motor for shifting said capacity controlling means against said bias; a cylinder; a piston reciprocable in said cylinder and defining therein an impulse space; a connection from said impulse space to said motor; a valve coacting with said piston to control a free vent from the impulse space, said valve being adjustable to vary its control point with reference to the piston stroke; means responsive to pressure developed by operation of said compressor for adjusting said valve; means for reciprocating said piston in timed relation to the cycles of the compressor; a relief valve for permitting relief of excess pressure developed in the impulse space; an inlet valve for the impulse space; a member yieldingly biased to hold open the inlet valve just named; a lubricating pump arranged to be driven when the compressor ,1. operates; a pressure motor arranged to retract said yieldingly biased member; and an asymmetric flow connection between the discharge of said lubricating pump and said pressure motor and arranged to delay response of the motor to rising pressure.

WOLFGANG TURNWALD.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,606,060 Cox Nov. 9, 1926 2,134,835 Nordberg Nov, 1, 1938 2,137,219 Aikman Nov. 22, 1938 2,159,815 McCune May 23, 1939 

